JP2005337393A - Reduction gear for driving water gate door - Google Patents

Reduction gear for driving water gate door Download PDF

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JP2005337393A
JP2005337393A JP2004157712A JP2004157712A JP2005337393A JP 2005337393 A JP2005337393 A JP 2005337393A JP 2004157712 A JP2004157712 A JP 2004157712A JP 2004157712 A JP2004157712 A JP 2004157712A JP 2005337393 A JP2005337393 A JP 2005337393A
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gear
reduction
external gear
shaft
driving
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Yasumasa Yamazaki
泰正 山▲崎▼
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Sumitomo Heavy Industries Ltd
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Sumitomo Heavy Industries Ltd
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Abstract

<P>PROBLEM TO BE SOLVED: To provide a compact and efficient reduction gear for driving a water gate door. <P>SOLUTION: A driving device D for the water gate door 46 is provided with a motor 38 and a reduction gear 40 for reducing rotation of the motor 38. The reduction gear 40 has an external gear and an internal gear having a small difference of the number of tooth between the external gear and to be internally engaged with the external gear. This reduction gear of an internal engagement type planetary gear mechanism takes a relative rotating component of the external gear and the internal gear as an output, and this reduction gear is provided with a first speed reducing part 40A having 86 % or more of efficiency and a second speed reducing part 40B of a parallel shaft gear mechanism having an input shaft connected to an output member of the first speed reducing part 40A and an output shaft 42 of the reduction gear for driving a water gate 46. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

本発明は、水門扉を駆動する駆動装置に適用される減速機に関する。   The present invention relates to a reduction gear applied to a drive device that drives a sluice door.

河川や水路における水の流れや流量を制御するために用いられる水門扉は、従来は手動によって操作されることが多かったが、近年ではモータを用いた電動式の駆動装置が普及してきている。   In the past, sluice doors used to control the flow and flow rate of water in rivers and waterways were often manually operated, but in recent years, electric drive devices using motors have become widespread.

図７に、この種の水門扉の駆動装置の一例を示す。この駆動装置２は、モータ３の回転を減速機４にて減速し、該減速機４の両サイドに延在させた駆動シャフト６にその減速出力を取り出す構成とされている。駆動シャフト６には、一対のドラムギヤ８が装着されており、該ドラムギヤ８を介して水門扉（図示略）に連結されたロープが巻回されている一対のドラム１０がそれぞれ駆動される構成とされている。   FIG. 7 shows an example of this type of sluice door drive device. The drive device 2 is configured to decelerate the rotation of the motor 3 with a speed reducer 4 and extract the speed reduction output to drive shafts 6 extended on both sides of the speed reducer 4. A pair of drum gears 8 is mounted on the drive shaft 6, and a pair of drums 10 around which a rope connected to a sluice gate (not shown) is wound are driven via the drum gear 8. Has been.

図８に示されるように、この種の水門扉の駆動装置に用いる減速機４としては、４段〜５段の平行軸歯車減速機構を用いた構造が用いられていた。これは、用途の特性上、減速機４の減速比として１／５００以上、場合によっては１／２５００程度までの高い値が求められるためである（例えば特許文献１参照）。なお、図８は、減速機４の上側ケーシング（図示略）を取り除いた状態を平面視したものである。   As shown in FIG. 8, a structure using a 4-stage to 5-stage parallel shaft gear reduction mechanism has been used as the speed reducer 4 used in this kind of sluice door drive device. This is because a high value of 1/500 or more, and in some cases up to about 1/2500 is required as the reduction ratio of the reduction gear 4 due to the characteristics of the application (see, for example, Patent Document 1). FIG. 8 is a plan view of a state in which the upper casing (not shown) of the speed reducer 4 is removed.

この減速機４では、入力軸１２、第１〜第３中間軸１４、１６、１８及び出力軸２０が水平且つ平行に配置されている。各軸１２、１４、１６、１８、２０は、平歯車（またはヘリカル歯車）によって構成される第１〜第４ピニオン２２、２４、２６、２８及び該第１〜第４ピニオン２２、２４、２６、２８とそれぞれ噛合する第１〜第４ギヤ３０、３２、３４、３６によって順次連結されている。   In the speed reducer 4, the input shaft 12, the first to third intermediate shafts 14, 16, 18 and the output shaft 20 are arranged horizontally and in parallel. Each of the shafts 12, 14, 16, 18, and 20 includes first to fourth pinions 22, 24, 26, and 28 and first to fourth pinions 22, 24, and 26 that are constituted by spur gears (or helical gears). , 28 are sequentially connected by first to fourth gears 30, 32, 34, 36 that mesh with each other.

なお、図の符号３７は下側ケーシング、１２Ａ、１４Ａ、１６Ａ、１８Ａ、２０Ａは、それぞれ入力軸１２、第１〜第３中間軸１４、１６、１８、出力軸２０を受ける軸受孔である。   Reference numeral 37 in the figure denotes a lower casing, and 12A, 14A, 16A, 18A, and 20A denote bearing holes that receive the input shaft 12, the first to third intermediate shafts 14, 16, 18, and the output shaft 20, respectively.

特開２００３−７４７８９号公報JP 2003-74789 A

しかしながら、このような平行軸歯車減速機構を用いた構造は、１／５００以上の減速比を必要とする水門扉の駆動装置に用いる減速機の構造としては、大きく且つ重くなり易いという問題があった。   However, the structure using such a parallel shaft gear reduction mechanism has a problem that the structure of the reduction gear used for a sluice door drive device that requires a reduction ratio of 1/500 or more tends to be large and heavy. It was.

また、このように４段〜５段の平行軸歯車を配置する場合、ケーシングへの組み込みという製造上の要請から、各軸は、水平に並べられることが多い。これは、上述の例のように、ケーシングを水平な分割線に沿って上側ケーシングと下側ケーシング３７とに分割し、下側ケーシング３７に形成された半円状の軸受孔１２Ａ〜２０Ａに各軸１２〜２０を「載置」し、この状態で、同じく対応する半円状の軸受孔（図示略）が形成された上側ケーシングを被せると、各軸１２〜２０の組み込みが容易に行えるためである。そのため、とりわけこの製造方法によって製造された減速機の場合、該減速機の幅方向の長さＷが大きくなってしまい易いという問題があった。   In addition, when four to five parallel shaft gears are arranged in this way, the shafts are often arranged horizontally because of the manufacturing requirement of incorporation into the casing. This is because the casing is divided into an upper casing and a lower casing 37 along a horizontal dividing line as in the above-described example, and the semicircular bearing holes 12A to 20A formed in the lower casing 37 are separated from each other. If the shafts 12 to 20 are “mounted” and an upper casing in which a corresponding semicircular bearing hole (not shown) is similarly formed is put in this state, the shafts 12 to 20 can be easily assembled. It is. Therefore, especially in the case of a speed reducer manufactured by this manufacturing method, there is a problem that the length W in the width direction of the speed reducer tends to increase.

本発明は、このような従来の問題を解消するためになされたものであって、必要な減速比を２段〜３段程度の減速機構で構成することができ、コンパクトで、且つ効率が犠牲にならない水門扉の駆動用減速機を提供することその課題としている。   The present invention has been made in order to solve such a conventional problem, and a required reduction ratio can be constituted by a reduction mechanism of about two to three stages, which is compact and sacrifices efficiency. An object of the present invention is to provide a speed reducer for driving a sluice gate that does not become a problem.

本発明は、水門扉を開閉駆動する駆動装置の減速機において、外歯歯車と、該外歯歯車と僅少の歯数差を有し、該外歯歯車が内接噛合する内歯歯車と、を備え、該外歯歯車と内歯歯車との相対回転成分を出力として取り出す内接噛合遊星歯車機構の減速部であって、その駆動効率が８６％以上の第１の減速部と、該第１減速部の出力部材と連結された入力軸と、前記水門を駆動する減速機出力軸を有する平行軸歯車機構の第２の減速部と、を備えたことにより、上記課題を解決したものである。   The present invention relates to a reduction gear for a drive device that opens and closes a sluice door, an external gear, an internal gear that has a slight difference in the number of teeth from the external gear, and the external gear meshes internally. A reduction gear part of an intermeshing planetary gear mechanism for taking out the relative rotational component between the external gear and the internal gear as an output, the first reduction part having a drive efficiency of 86% or more, and the first reduction part An input shaft connected to an output member of one speed reduction portion and a second speed reduction portion of a parallel shaft gear mechanism having a speed reducer output shaft for driving the water gate, thereby solving the above-mentioned problem. is there.

本発明においては、水門扉の駆動用減速機として、内接噛合遊星歯車機構であってその駆動効率が８６％以上の第１減速部と、平行軸歯車機構の第２減速部とで構成するようにした。内接噛合遊星歯車機構は、外歯歯車と、該外歯歯車と僅少の歯数差を有し該外歯歯車が内接噛合する内歯歯車と、を備え、該外歯歯車と内歯歯車との相対回転成分を出力として取り出すもので、１段で数十〜百数十という大きな減速比を得ることができる。そのため全体で２段〜３段程度の減速段で水門扉の駆動用減速機として必要な減速比を得ることができる。   In the present invention, as a drive speed reducer for a sluice gate, an intermeshing planetary gear mechanism having a driving efficiency of 86% or more and a second speed reduction part of a parallel shaft gear mechanism is configured. I did it. An internal meshing planetary gear mechanism includes an external gear, and an internal gear that has a slight difference in the number of teeth from the external gear and that meshes with the external gear, and the external gear and the internal gear It takes out the relative rotation component with the gear as an output, and a large reduction ratio of several tens to several hundreds can be obtained in one stage. Therefore, a reduction ratio required as a drive speed reducer for a sluice door can be obtained with a total of about 2 to 3 reduction stages.

また、後述するように、内接噛合遊星歯車機構は、相応の工夫を施すことにより、比較的容易に駆動効率の高い減速機構とすることができる。そのため、全体として軽量・コンパクトで且つ駆動効率の高い減速機を得ることができる。   Further, as will be described later, the intermeshing planetary gear mechanism can be made a reduction mechanism with high driving efficiency relatively easily by applying appropriate measures. For this reason, it is possible to obtain a reduction gear that is light and compact as a whole and has high driving efficiency.

さらには、第２減速部として減速比の設定等の自由度が高い平行軸歯車機構を組み合わせるようにしてあるため、さまざまな水門扉に対して最適な減速比およびトルクに調整するのが容易である。   Furthermore, since a parallel shaft gear mechanism having a high degree of freedom such as setting of the reduction ratio is combined as the second reduction part, it is easy to adjust the optimum reduction ratio and torque for various sluice doors. is there.

水門扉を駆動するために用いる減速機として、より軽量且つコンパクトで、高い駆動効率を維持することできる減速機を提供することができる。   As a speed reducer used for driving the sluice gate, a speed reducer that is lighter and more compact and can maintain high driving efficiency can be provided.

以下図面に基づいて、本発明の実施形態の一例に係る水門扉の駆動用減速機が適用された水門扉の駆動装置について詳細に説明する。   Hereinafter, a sluice door drive apparatus to which a sluice door drive speed reducer according to an example of an embodiment of the present invention is applied will be described in detail with reference to the drawings.

図１は、当該駆動装置Ｄの概略構成図である。この駆動装置Ｄは、モータ３８と、当該モータ３８の回転を減速する減速機４０と、該減速機４０の出力軸（図１においては一方側のみ図示）４２と連結されたドラム４４と、水門扉４６に連結され、該ドラム４４の回転によってワイヤロープ４８を介して上下動可能とされたシーブ５０とから主に構成されている。   FIG. 1 is a schematic configuration diagram of the driving device D. The driving device D includes a motor 38, a speed reducer 40 that decelerates the rotation of the motor 38, a drum 44 that is connected to an output shaft 42 (only one side is shown in FIG. 1), water, The sheave 50 is mainly composed of a sheave 50 connected to the gate door 46 and capable of moving up and down via a wire rope 48 by the rotation of the drum 44.

前記モータ３８の出力軸３８Ａは、カップリング５２を介して減速機４０と連結されている。減速機４０は、図２及び図３に示されるように、その初段に内接噛合遊星歯車機構の第１減速部４０Ａを有する。この第１変速部４０Ａの構成については後に詳述する。   The output shaft 38 </ b> A of the motor 38 is connected to the speed reducer 40 via a coupling 52. As shown in FIGS. 2 and 3, the speed reducer 40 has a first speed reducing portion 40 </ b> A of an intermeshing planetary gear mechanism at the first stage. The configuration of the first transmission unit 40A will be described in detail later.

第１減速部４０Ａの出力軸（図２、図３では図示略：後述）は、取付フランジ５２を介して第２減速部４０Ｂの入力軸を構成する第１中間軸５４（図３参照）と連結されている。第２減速部４０Ｂは、この実施形態では、該第１中間軸５４のほかに第２中間軸５６及び前記減速機４０の出力軸４２を備え、図示せぬヘリカルピニオン及びヘリカルギヤの組合せにより２段の減速を行うヘリカル平行軸歯車機構を構成している。   An output shaft (not shown in FIGS. 2 and 3; described later) of the first reduction gear 40A is connected to a first intermediate shaft 54 (see FIG. 3) constituting an input shaft of the second reduction gear 40B via a mounting flange 52. It is connected. In this embodiment, the second reduction gear 40B includes a second intermediate shaft 56 and the output shaft 42 of the speed reducer 40 in addition to the first intermediate shaft 54. The second reduction portion 40B has two stages by a combination of a helical pinion and a helical gear (not shown). The helical parallel shaft gear mechanism for reducing the speed is configured.

図１に戻って、出力軸４２は、カップリング５７、駆動シャフト５８を介して水門扉４６をワイヤ駆動するための前記ドラム４４と連結されている。   Returning to FIG. 1, the output shaft 42 is connected to the drum 44 for driving the sluice door 46 through a coupling 57 and a drive shaft 58.

図４に第１減速部４０Ａの詳細構成を示す。なお、図５は図４の矢視Ｖ−Ｖ線に沿う断面図である。   FIG. 4 shows a detailed configuration of the first reduction part 40A. 5 is a cross-sectional view taken along the line VV in FIG.

この第１減速部４０Ａは、外歯歯車６０、該外歯歯車６０と僅少の歯数差を有し、該外歯歯車６０が内接噛合する内歯歯車６２を備える、いわゆる内接噛合遊星歯車機構の減速構造が採用されている。外歯歯車６０が（１８０度位相をずらして）軸方向に２枚配置されているのは、容量の増大を図ったためである。   The first reduction gear portion 40A includes an external gear 60 and a so-called internal meshing planetary planet that has a slight difference in the number of teeth from the external gear 60 and includes an internal gear 62 with which the external gear 60 meshes internally. A gear mechanism reduction structure is employed. The reason why two external gears 60 are arranged in the axial direction (with a phase difference of 180 degrees) is to increase the capacity.

この実施形態では、内歯歯車６２がケーシング６３と一体化して固定されており、出力としての外歯歯車６０と内歯歯車６２の相対回転成分が、外歯歯車６０側から出力される構成とされている。外歯歯車６０の歯数は、この実施形態では７８、内歯歯車６２の歯数は８０であり、両者６０、６２の歯数は僅少の歯数差（この例では２）に設定されている。なお、「僅少の歯数差」とは、６以下をいう。内歯歯車６２の内歯６２Ａは、この実施形態ではローラピンによって構成されている。   In this embodiment, the internal gear 62 is integrally fixed with the casing 63, and the relative rotational component of the external gear 60 and the internal gear 62 as an output is output from the external gear 60 side. Has been. The number of teeth of the external gear 60 is 78 in this embodiment, the number of teeth of the internal gear 62 is 80, and the number of teeth of both the gears 60 and 62 is set to a slight difference (2 in this example). Yes. “Slight difference in the number of teeth” means 6 or less. In this embodiment, the internal teeth 62A of the internal gear 62 are constituted by roller pins.

この第１減速部４０Ａの駆動効率、即ち、（実出力トルク）／（実入力トルク×減速比）は、以下のような構成が採用されることにより、約９０％程度（＞８６％）が確保されている。   The drive efficiency of the first reduction gear 40A, that is, (actual output torque) / (actual input torque × reduction ratio) is about 90% (> 86%) by adopting the following configuration. It is secured.

すなわち、この実施形態に係る第１減速部４０は、前記外歯歯車６０及び内歯歯車６２のほか、入力軸６４、偏心体６６を有する３本の偏心体軸６８、及び外歯歯車６０の両側に配置された第１、第２支持ブロック７６、７８を主な構成要素として備える。   That is, the first reduction gear 40 according to this embodiment includes the external gear 60 and the internal gear 62, the input shaft 64, the three eccentric body shafts 68 having the eccentric body 66, and the external gear 60. First and second support blocks 76 and 78 arranged on both sides are provided as main components.

入力軸６４は、カップリング５２（図１参照）によりモータ３８の出力軸３８Ａと連結され、第１減速部４０Ａの半径方向中央に配置されている。入力軸６４の先端には、ピニオン６４Ａが一体的に形成されている。   The input shaft 64 is connected to the output shaft 38A of the motor 38 by a coupling 52 (see FIG. 1), and is disposed at the center in the radial direction of the first reduction gear 40A. A pinion 64 </ b> A is integrally formed at the tip of the input shaft 64.

ピニオン６４Ａは、３本の偏心体軸６８にそれぞれ組み込まれた伝動歯車７０と噛合しており、該ピニオン６４Ａの回転によって伝動歯車７０を介して該３本の偏心体軸６８が同時に従動回転可能である。   The pinion 64A meshes with the transmission gears 70 incorporated in the three eccentric body shafts 68, respectively, and the three eccentric body shafts 68 can be driven and rotated simultaneously via the transmission gear 70 by the rotation of the pinion 64A. It is.

偏心体軸６８は、外歯歯車６０を偏心回転させるための偏心体６６をそれぞれ有し、入力軸６４と平行に配置されている。各偏心体軸６８は、偏心体軸ベアリング７４を介して外歯歯車６０の両側に配置された前記第１、第２支持ブロック７６、７８に回転自在に両持ち支持されている。偏心体軸６８に一体的に装着された偏心体６６は、偏心体ベアリング８０を介して外歯歯車６０の偏心体軸孔６０Ａと嵌合している。各偏心体軸６８の偏心体６６は、その偏心位相が揃えられている。このため、偏心体軸６８が回転して偏心体６６が偏心回転することにより、外歯歯車６０を該偏心体６６の偏心位相の回転に追従させる態様で内歯歯車６２に内接しながら揺動回転させることが可能である。   The eccentric body shaft 68 has an eccentric body 66 for rotating the external gear 60 eccentrically, and is disposed in parallel with the input shaft 64. Each eccentric body shaft 68 is rotatably supported by the first and second support blocks 76 and 78 disposed on both sides of the external gear 60 via an eccentric body shaft bearing 74. The eccentric body 66 mounted integrally with the eccentric body shaft 68 is fitted into the eccentric body shaft hole 60 </ b> A of the external gear 60 via the eccentric body bearing 80. The eccentric bodies 66 of the eccentric body shafts 68 have the same eccentric phase. For this reason, the eccentric body shaft 68 rotates and the eccentric body 66 rotates eccentrically, so that the external gear 60 swings while being inscribed in the internal gear 62 in a manner to follow the rotation of the eccentric phase of the eccentric body 66. It is possible to rotate.

各偏心体軸６８を回転自在に支持している第１、第２支持ブロック７６、７８は、ブロックベアリング８２を介してケーシング６３に回転自在に支持されている。また、第１、第２支持ブロック７６、７８は、それぞれキャリヤピン８６（及びボルト８４）を介して連結され、相互に一体化されている。   The first and second support blocks 76 and 78 that rotatably support the eccentric body shafts 68 are rotatably supported by the casing 63 via block bearings 82. The first and second support blocks 76 and 78 are connected to each other via carrier pins 86 (and bolts 84), and are integrated with each other.

第１、第２支持ブロック７６、７８は、第１減速部４０Ａの出力部材に相当しており、取付フランジ５９を介して第２減速部４０Ｂの前記第１中間軸５４とボルト８４を介して連結されている。   The first and second support blocks 76 and 78 correspond to an output member of the first speed reducing portion 40A, and via the mounting flange 59, the first intermediate shaft 54 and the bolt 84 of the second speed reducing portion 40B. It is connected.

次に、この駆動装置Ｄの作用を説明する。   Next, the operation of the drive device D will be described.

モータ３８のモータ軸３８Ａが回転すると、カップリング５２を介して減速機４０の第１減速部４０Ａの入力軸６４が回転する。   When the motor shaft 38 </ b> A of the motor 38 rotates, the input shaft 64 of the first speed reduction unit 40 </ b> A of the speed reducer 40 rotates via the coupling 52.

入力軸６４が回転すると、該入力軸６４と噛合している伝動歯車７０を介して３本の偏心体軸６８が同時に減速回転し、それぞれの偏心体軸６８に一体的に装着されている偏心体６６が同位相で回転する。この結果、外歯歯車６０が内歯歯車６２に内接しながら揺動回転する。内歯歯車６２はケーシング６３と一体化され、固定された状態にあるため、入力軸６４が１回転すると偏心体６６を介して外歯歯車６０側が揺動回転し、該外歯歯車６０と内歯歯車６２の噛合位置が順次ずれて１回転する。このとき、外歯歯車６０は内歯歯車６２よりも歯数が２だけ少ないため、固定状態にある内歯歯車６２に対して２／（外歯歯車６０の歯数）、すなわちこの実施形態の場合２／８０に相当する分だけ位相がずれる（自転する）ことになる。そのため、偏心体軸６８が該自転成分に相当する速度で入力軸６４の回りを公転することになり、該偏心体軸６８を支持している第１、第２支持ブロック７６、７８が当該公転速度に相当する速度で回転する。第１、第２支持ブロック７６、７８は、キャリヤピン８６を介して相互に連結されており、第２支持ブロック７８が第２減速部４０Ｂの入力軸である第１中間軸５４と取付フランジ５９を介して連結されているため、第１、第２支持ブロック７６、７８の回転はそのまま第２減速部４０Ｂの第１中間軸５４に伝達される。第２減速部４０Ｂでは、この第１中間軸５４の回転を更に２段減速し、出力軸４２から出力する。出力軸４２が回転すると、カップリング５７を介して駆動シャフト５８が回転し、ドラム４４が回転する。この結果ワイヤ４８を介して水門扉４６に固定されたシーブ５０が回転し、当該シーブ５０の上下動と共に水門扉４６が上下動（開閉）する。   When the input shaft 64 is rotated, the three eccentric body shafts 68 are simultaneously decelerated and rotated through the transmission gears 70 meshed with the input shaft 64, and are eccentrically attached to the eccentric body shafts 68. The body 66 rotates in the same phase. As a result, the external gear 60 swings and rotates while being inscribed in the internal gear 62. Since the internal gear 62 is integrated with the casing 63 and is in a fixed state, when the input shaft 64 rotates once, the external gear 60 side swings and rotates via the eccentric body 66, and the external gear 60 and the internal gear 60 are rotated. The meshing position of the toothed gear 62 is sequentially shifted and rotated once. At this time, since the external gear 60 has two teeth less than the internal gear 62, the external gear 60 is 2 / (the number of teeth of the external gear 60) with respect to the fixed internal gear 62, that is, in this embodiment. In this case, the phase shifts (rotates) by an amount corresponding to 2/80. For this reason, the eccentric body shaft 68 revolves around the input shaft 64 at a speed corresponding to the rotation component, and the first and second support blocks 76 and 78 supporting the eccentric body shaft 68 perform the revolution. It rotates at a speed equivalent to the speed. The first and second support blocks 76 and 78 are connected to each other via a carrier pin 86, and the second support block 78 is a first intermediate shaft 54 that is an input shaft of the second reduction unit 40 </ b> B and a mounting flange 59. Therefore, the rotations of the first and second support blocks 76 and 78 are transmitted to the first intermediate shaft 54 of the second reduction gear 40B as it is. In the second reduction part 40B, the rotation of the first intermediate shaft 54 is further reduced by two stages and output from the output shaft 42. When the output shaft 42 rotates, the drive shaft 58 rotates through the coupling 57, and the drum 44 rotates. As a result, the sheave 50 fixed to the sluice door 46 rotates via the wire 48, and the sluice door 46 moves up and down (opens and closes) as the sheave 50 moves up and down.

この実施形態における第１減速部４０Ａは、外歯歯車６０の両側に第１、第２支持ブロック７６、７８を有し、３本の偏心体軸６８をこの第１、第２支持ブロック７６、７８によって両持ち支持するようにしているため、支持剛性が高く、外歯歯車６０を安定した状態で揺動回転させることができる。また、各偏心体軸６８は第１、第２支持ブロック７６、７８に偏心体軸ベアリング７４を介して支持されており、且つ、各偏心体６６と外歯歯車６０も偏心体ベアリング８０を介して互いに嵌合している。そのため、各要素は極めて円滑に回転することができ、この結果、この第１減速部４０Ａ に於ける部分の駆動効率を９０％以上にまで高めることができている。ヘリカル平行軸歯車構造の第２減速部４０Ｂは、もともと第１減速部４０Ａよりも高い駆動効率を容易に実現できるため、この減速機４０は、結果として非常に高い駆動効率を確保できる。   The first speed reducing portion 40A in this embodiment has first and second support blocks 76 and 78 on both sides of the external gear 60, and three eccentric body shafts 68 are connected to the first and second support blocks 76, Since both ends are supported by 78, the support rigidity is high, and the external gear 60 can be rotated and rotated in a stable state. Each eccentric body shaft 68 is supported by the first and second support blocks 76 and 78 via an eccentric body shaft bearing 74, and each eccentric body 66 and the external gear 60 are also connected via the eccentric body bearing 80. Are engaged with each other. Therefore, each element can rotate very smoothly, and as a result, the driving efficiency of the portion in the first reduction gear 40A can be increased to 90% or more. Since the second reduction part 40B having the helical parallel shaft gear structure can easily achieve higher driving efficiency than the first reduction part 40A, the reduction gear 40 can ensure a very high driving efficiency as a result.

尤も、本発明においては、内接噛合遊星歯車構造の具体的な構成については特にこの構成に限定されない。要は、結果として８６％以上の高い駆動効率が確保されればよい。例えば、図示はしないが、内接噛合遊星歯車構造として、外歯歯車に形成した貫通孔に遊嵌する内ピンから出力を取り出す、いわゆる内ピン取りだしタイプの内接噛合遊星歯車構造を採用した場合には、該内ピンと貫通孔との摺動抵抗を小さくするべく、内ピンの周りに内ローラを配置するのは駆動効率を高める手法として有効である。また、外歯歯車の歯面を鏡面仕上げする等の方法も、駆動効率を高める手法として有効である。なお、８６％以上という効率は、水門扉４６を合理的な容量の駆動源（モータ等）で駆動するために必要な効率である。   However, in the present invention, the specific configuration of the intermeshing planetary gear structure is not particularly limited to this configuration. In short, it is only necessary to ensure a high driving efficiency of 86% or more as a result. For example, although not shown, when an internal mesh planetary gear structure of a so-called internal pin take-out type that takes out output from an internal pin loosely fitted in a through hole formed in an external gear is adopted as the internal mesh planetary gear structure. In order to reduce the sliding resistance between the inner pin and the through hole, it is effective as a method for increasing the driving efficiency to arrange the inner roller around the inner pin. Further, a method of mirror-finishing the tooth surface of the external gear is also effective as a method for improving the driving efficiency. The efficiency of 86% or more is an efficiency necessary for driving the sluice door 46 with a drive source (motor or the like) having a reasonable capacity.

また、本発明における内接噛合遊星歯車構造の中には、外歯歯車が半径方向に変形可能な素材で形成されており、該外歯歯車の変形位置（内歯歯車との噛合位置）を順次回転させることによって、外歯歯車と内歯歯車の相対回転出力を得る構成も含まれる。このタイプは、いわゆる「撓み噛み合い式の内接噛合遊星歯車構造」と称されるもので、同様に外歯歯車と内歯歯車の（歯数差／外歯歯車の歯数）に依存する減速比を得ることができる。   Further, in the internal meshing planetary gear structure according to the present invention, the external gear is formed of a material that can be deformed in the radial direction, and the deformation position of the external gear (meshing position with the internal gear) is determined. A configuration in which a relative rotational output between the external gear and the internal gear is obtained by sequentially rotating is also included. This type is a so-called “flexion-meshing internal meshing planetary gear structure”. Similarly, the speed reduction depends on the difference between the external gear and the internal gear (the difference in the number of teeth / the number of teeth of the external gear). A ratio can be obtained.

また、上記実施形態においては、外歯歯車と内歯歯車の歯数差を「２」に設定した例が示されていたが、本発明においては、例えば図６に示されるように、歯数差が１に設定されている内接噛合遊星歯車構造の場合であっても、適用可能である。歯数差が１の第１減速部は、歯数差２の第１減速部に対し、効率は若干低下するが、減速比は２倍の値を確保できる。逆に歯数差を３以上に設定したときは、歯数差が２の場合に比べて得られる減速比は小さくなるが、効率をより高めることができる。なお、図６におけるその他の構成については、先の実施形態と同様であるため、図中において同一又は類似する部分に下２桁が同一の符号を付すにとどめ、重複説明を省略する。   In the above embodiment, an example in which the difference in the number of teeth between the external gear and the internal gear is set to “2” is shown. However, in the present invention, for example, as shown in FIG. Even in the case of an intermeshing planetary gear structure in which the difference is set to 1, it is applicable. Although the efficiency of the first speed reduction part with a tooth number difference of 1 is slightly lower than that of the first speed reduction part with a tooth number difference of 2, the reduction ratio can be doubled. Conversely, when the difference in the number of teeth is set to 3 or more, the speed reduction ratio obtained is smaller than that in the case where the difference in the number of teeth is 2, but the efficiency can be further increased. Since the other configurations in FIG. 6 are the same as those in the previous embodiment, the same or similar parts in the figure are given the same reference numerals in the last two digits, and redundant description is omitted.

本発明は、水門扉を駆動するための駆動装置に使用する減速機に適用可能である。   The present invention is applicable to a speed reducer used in a drive device for driving a sluice door.

本発明の実施形態の一例に係る減速機が適用された水門扉の駆動装置を示す概略構成図The schematic block diagram which shows the drive device of the sluice door to which the reduction gear which concerns on an example of embodiment of this invention was applied. 上記駆動装置における減速機の全体構成を示す平面図The top view which shows the whole structure of the reduction gear in the said drive device 同側面図Side view 同減速機の内部構成を示す断面図Sectional view showing the internal configuration of the reducer 図４の矢視Ｖ−Ｖ線に沿う断面図Sectional drawing which follows the arrow VV line of FIG. 本発明の他の実施形態に係る減速機を示す図５相当の断面図Sectional drawing equivalent to FIG. 5 which shows the reduction gear concerning other embodiment of this invention. 従来の減速機が組み込まれた水門扉の駆動装置を示す概略構成図Schematic configuration diagram showing a sluice door drive device incorporating a conventional speed reducer 該従来の減速機の内部構成を示す平面図The top view which shows the internal structure of this conventional reduction gear

符号の説明Explanation of symbols

Ｄ…駆動装置
３８…モータ
４０…減速機
４０Ａ…第１減速部
４０Ｂ…第２減速部
４２…出力軸
４４…ドラム
４６…水門扉
４８…ワイヤロープ
５０…シーブ
５２…カップリング
５４…第１中間軸
５６…第２中間軸
５８…駆動シャフト
６０…外歯歯車
６２…内歯歯車
６４…入力軸
６８…偏心体軸
７０…伝動歯車
７２…偏心体
７４…偏心体ベアリング
７６…第１支持ブロック
７８…第２支持ブロック
８０…偏心体ベアリング
８２…ブロックベアリング
８４…ボルト D ... Drive device 38 ... Motor 40 ... Reducer 40A ... First reduction part 40B ... Second reduction part 42 ... Output shaft 44 ... Drum 46 ... Sluice door 48 ... Wire rope 50 ... Sheave 52 ... Coupling 54 ... First intermediate Shaft 56 ... Second intermediate shaft 58 ... Drive shaft 60 ... External gear 62 ... Internal gear 64 ... Input shaft 68 ... Eccentric body shaft 70 ... Transmission gear 72 ... Eccentric body 74 ... Eccentric body bearing 76 ... First support block 78 ... Second support block 80 ... Eccentric body bearing 82 ... Block bearing 84 ... Bolt

Claims (3)

水門扉を駆動する駆動装置に使用する減速機において、
外歯歯車と、該外歯歯車と僅少の歯数差を有し該外歯歯車が内接噛合する内歯歯車と、を備え、該外歯歯車と内歯歯車との相対回転成分を出力として取り出す内接噛合遊星歯車機構の減速部であって、その駆動効率が８６％以上の第１の減速部と、
該第１の減速部の出力部材と連結された入力軸と、前記水門扉を駆動する減速機出力軸とを有する平行軸歯車機構の第２の減速部と、
を備えたことを特徴とする水門扉の駆動用減速機。 In the reducer used in the drive device that drives the sluice gate,
An external gear, and an internal gear that has a slight difference in the number of teeth from the external gear and that is internally meshed with the external gear, and outputs a relative rotational component between the external gear and the internal gear. A first reduction gear portion having a driving efficiency of 86% or more, which is a reduction gear portion of the intermeshing planetary gear mechanism to be taken out as
A second reduction part of a parallel shaft gear mechanism having an input shaft connected to the output member of the first reduction part and a reduction gear output shaft for driving the water gate;
A sluice door drive speed reducer characterized by comprising: 請求項１において、
前記第１の減速部が、
入力軸と、
前記外歯歯車を偏心回転させる偏心体をそれぞれ備え、前記入力軸の回転によって従動回転する複数の偏心体軸と、
前記外歯歯車の軸方向両側に回転自在にそれぞれ配置され、前記偏心体軸を回転自在に両持ち支持すると共に、前記外歯歯車を貫通するキャリヤ体を介して互いに連結された第１、第２支持ブロックとを備え、
該第１、第２支持ブロックが出力部材とされた構成の減速部である水門扉の駆動用減速機。 In claim 1,
The first reduction part is
An input shaft;
A plurality of eccentric body shafts each including an eccentric body that eccentrically rotates the external gear, and rotated by the rotation of the input shaft;
First and second, which are rotatably arranged on both sides in the axial direction of the external gear, respectively support the eccentric body shaft rotatably, and are connected to each other via a carrier body penetrating the external gear. 2 support blocks,
A speed reducer for driving a sluice door, which is a speed reducing portion having a configuration in which the first and second support blocks are output members. 請求項１または２において、
前記外歯歯車と内歯歯車との前記歯数差が２である、水門扉の駆動用減速機。 In claim 1 or 2,
A speed reducer for driving a sluice door, wherein the difference in the number of teeth between the external gear and the internal gear is two.
JP2004157712A 2004-05-27 2004-05-27 Reduction gear for driving water gate door Pending JP2005337393A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007292248A (en) * 2006-04-26 2007-11-08 Sumitomo Heavy Ind Ltd Inscribed meshing type planetary gear unit
JP7397539B2 (en) 2018-10-25 2023-12-13 株式会社ユーテック reduction gear

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007292248A (en) * 2006-04-26 2007-11-08 Sumitomo Heavy Ind Ltd Inscribed meshing type planetary gear unit
JP7397539B2 (en) 2018-10-25 2023-12-13 株式会社ユーテック reduction gear

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